JP2012017921A - Heat exchanger and intake air cooling system of engine using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger, the performance of which is improved by changing a shape of a tube comparatively easily without arranging a guide vane in an inlet-side tank, so that a fluid is restrained from flowing partially to a part of tubes.SOLUTION: A plurality of tubes 21a-23a, in each of which a flat passage for passing the fluid is formed, are extended horizontally and arranged vertically at intervals. A plurality of fins 24, each of which is formed in such a corrugated shape that the fin is contacted alternately with the adjacent tubes, are arranged, so that the fin is placed between the adjacent tubes. Fluid inlets of the plurality of tubes are connected communicatively to the single inlet-side tank and fluid outlets of the plurality of tubes are connected communicatively to a single outlet-side tank 26. A fluid introduction port is formed on the inlet-side tank and a fluid discharge port is formed on the outlet-side tank. The tube 21a opposed to the fluid introduction port is formed to have the smallest hole area in the horizontal stage thereof and the tube 22a or 23a is formed to have the hole area which is made larger stepwise in each of a plurality of horizontal stages thereof as the horizontal stage is apart vertically from the fluid introduction port.

Description

  The present invention relates to a heat exchanger that cools or heats a fluid with a heat medium, and an intake air cooling device for an engine that uses the heat exchanger.

Conventionally, the air passages in the inlet duct of the air cooler where the blower air discharge pipe or the blower outlet of the turbocharger and the air cooler communicate with each other with bending and area expansion are substantially equal by a plurality of main guide vanes. An inlet duct of a supercharged air cooler for a diesel engine in which a sub-guide vane is provided in each divided passage, and a sub guide vane is provided at a position closer to the inside of the curve within a range of 1/2 to 1/4 of the passage width. (For example, refer to Patent Document 1). In this supercharged air cooler for diesel engines, the high-temperature and high-pressure air discharged from the blower outlet of the turbocharger is introduced into the air cooling pipe through the air discharge pipe and the connection duct (inlet duct) and cooled there. The air is supplied to the air reservoir, and is distributed from the air reservoir to each cylinder. Further, the passage area is substantially divided by the main guide vane which is formed by the outer plate of the connecting duct and is bent corresponding to the bending of the outer plate of the connecting duct. Further, the air passage divided by the main guide vane is subdivided by the sub guide vane, the width of the passage corresponding to the outside of the bending of the sub guide vane is X _A, and the width of the passage corresponding to the inside of the bending of the sub guide vane is X _B X _A and X _B are set so as to satisfy the relational expression of 1/2> X _B / (X _A + X _B )> ¼.

  In the inlet duct of the supercharged air cooler for a diesel engine configured as described above, when the position of the sub guide vane is set to ½ to ¼ from the inside of the bending of each passage width, the pressure loss rapidly decreases. The pressure loss mitigating action is realized. In addition, this pressure loss mitigation action produces a uniform flow in the connection duct (inlet duct) at the same time, so that air flows through the entire passage area in the air cooler, improving the cooling effect and realizing the action of improving the cooling effect. The Further, since each passage has vibration response characteristics as different air columns with respect to the pulsation of the air supply system induced on the air reservoir side, a pulsation damping action that attenuates the pulsation of the air supply system is realized. As a result, the pressure loss mitigating action, cooling effect improving action and pulsation damping action satisfy the requirements as a low pressure loss, good cooling effect and low fluctuating pressure air supply system. Can be achieved.

Japanese Utility Model Laid-Open No. 50-56810 (Claim 1, specification, page 2, line 10 to page 15, line 15, specification, page 6, line 2 to page 14, line 14, specification, page 7, page 8) Line to page 11 line, specification page 8 line 16 to page 19 line, specification page 11 line 16 to page 19 line, specification page 13 line 6 to page 19 9 lines, Fig. 1 and Fig. 3)

  However, in the inlet duct of the supercharged air cooler for a diesel engine shown in the above-mentioned conventional patent document 1, the outer plate of the connection duct (inlet duct), the main guide vane, and the sub guide vane are bent with a predetermined curvature. Therefore, there is a problem in that the number of bending processes for these members increases and the number of welding steps for the main guide vane and the sub guide vane to the outer plate increases.

  The object of the present invention is to provide a relatively simple change in the shape of the tube without providing a guide vane in the inlet side tank, thereby suppressing the uneven flow of fluid to some tubes and improving the heat exchange performance. An object of the present invention is to provide a heat exchanger and an intake air cooling device for an engine using the heat exchanger.

  As shown in FIGS. 1 and 2, the first aspect of the present invention is a plurality of tubes in which flat passages are formed that extend in the horizontal direction and are spaced apart in the vertical direction and through which fluid passes. 21a to 23a, a plurality of fins 24 formed in a corrugated shape so as to alternately contact adjacent tubes 21a to 23a disposed between these tubes 21a to 23a, and fluids in the tubes 21a to 23a A single inlet side tank 25 provided on the inlet side and connected to fluid inlets of the plurality of tubes 21a to 23a, and a fluid outlet of the plurality of tubes 21a to 23a provided on the fluid outlet side of the tubes 21a to 23a A single outlet side tank 26 communicated with the inlet side tank 25, a fluid inlet 25 a formed in the inlet side tank 25 for introducing fluid into the inlet side tank 25, and formed in the outlet side tank 26. In the heat exchanger provided with the fluid discharge port 26a for discharging the fluid from the outlet side tank 26, the hole area in the horizontal stage of the tube 21a facing the fluid introduction port 25a among the plurality of tubes 21a to 23a is the largest. It is formed so as to be small, and the hole area of the tubes 22a and 23a is configured to increase for each of a plurality of horizontal stages or for each horizontal stage as the distance from the fluid introduction port 25a increases in the vertical direction.

  2nd viewpoint of this invention is invention based on 1st viewpoint, Comprising: As shown in FIG.1 and FIG.2, the multiple tubes 21a-23a have the same length, respectively, and multiple The tubes 21a to 23a have the same height, and a single tube or a plurality of tubes 21a to 23a are provided in the width direction so that the tubes 21a to 23a in each horizontal stage are within the same width. The number of tubes 21a in the horizontal stage facing the fluid inlet 25a is the largest, and the number of tubes 22a, 23a is increased for each of the plurality of horizontal stages or for each horizontal stage as the distance from the fluid inlet 25a in the vertical direction increases. It is characterized by being configured to be reduced.

  A third aspect of the present invention is an invention based on the first aspect, and as shown in FIGS. 4 and 5, the plurality of tubes 61a to 63a have the same length, and the plurality of tubes The tubes 61a to 63a have the same width, and the height of the tube 61a facing the fluid inlet 25a is the lowest among the plurality of tubes 61a to 63a, and is separated from the fluid inlet 25a in the vertical direction. Accordingly, the height of the tubes 62a, 63a is configured to be higher for each of the plurality of horizontal stages or for each horizontal stage.

  According to a fourth aspect of the present invention, as shown in FIG. 3, the heat exchanger according to any one of claims 1 to 3 is used as an intercooler 13 that cools the intake air compressed by the turbocharger 12. It is an intake air cooling device for an engine.

  According to a fifth aspect of the present invention, there is provided an intake air for an engine in which the heat exchanger according to any one of claims 1 to 3 is used as an EGR cooler for cooling EGR gas recirculated from the exhaust passage of the engine to the intake passage. It is a cooling device.

  In the heat exchanger according to the first aspect of the present invention, since the hole area in the horizontal stage of the tube facing the fluid inlet is the smallest, the flow resistance of the fluid passing through the tube facing the fluid inlet is reduced. Largest and difficult for fluids to pass through. Further, since the hole area of the tube is increased for each of the plurality of horizontal stages or for each horizontal stage as the distance from the fluid introduction port increases in the vertical direction, the fluid that passes through the tube as the distance from the fluid introduction port increases in the vertical direction. The flow resistance of the fluid becomes smaller and the fluid becomes easier to pass through. As a result, the fluid positively tries to pass through the tube that is separated from the fluid introduction port in the vertical direction, so that a bias that a large amount of fluid flows into the tube facing the fluid introduction port can be suppressed. Accordingly, since the fluid flows in a distributed manner over the plurality of tubes, the heat exchange performance of the heat exchanger can be improved. In addition, since the hole area in the horizontal stage of the tube facing the fluid introduction port is formed to be the smallest, the amount of fluid flowing into the tube facing the fluid introduction port is reduced and the tube where the fluid faces the fluid introduction port The resistance at the time of circulation increases, and the speed of the fluid decreases. As a result, since the fluid is efficiently cooled or heated by the refrigerant or the heat medium when the fluid passes through the tube facing the fluid inlet, the overall heat exchange performance of the heat exchanger is improved. You can also. Further, since the outer plate of the connection duct, the main guide vane and the sub guide vane are formed in a relatively complicated shape, the conventional supercharged air cooling for diesel engines that increases the number of processing steps and welding steps of these members. Compared with the inlet duct of the vessel, the present invention can suppress the deviation of the fluid flow to some tubes by changing the shape of the tubes relatively easily without providing guide vanes in the inlet side tank. , Heat exchange performance can be improved.

  In the heat exchanger according to the second aspect of the present invention, a single tube or a plurality of tubes in each horizontal stage are configured to be within the same width, and the number of tubes in the horizontal stage facing the fluid inlet is the largest. Since many are formed, the flow resistance of the fluid passing through the tube facing the fluid introduction port is the largest, and the fluid hardly passes. In addition, since the number of tubes decreases for each of the plurality of horizontal stages or for each horizontal stage as the distance from the fluid introduction port increases in the vertical direction, the flow of the fluid that passes through the tubes as the distance from the fluid introduction port increases in the vertical direction. The resistance becomes smaller and the fluid easily passes. As a result, similar to the above, the fluid actively attempts to pass through a tube that is vertically away from the fluid inlet, thus suppressing the bias that a large amount of fluid flows into the tube facing the fluid inlet. it can. In addition, a single tube or a plurality of tubes in each horizontal stage are configured to fit within the same width, and the number of tubes in the horizontal stage facing the fluid inlet is the largest, so that it faces the fluid inlet. As the amount of fluid flowing into the tube decreases, the resistance when the fluid flows through the tube facing the fluid inlet increases and the speed of the fluid decreases. As a result, as described above, when the fluid passes through the tube facing the fluid inlet, the fluid is efficiently cooled or heated by the refrigerant or the heat medium. The performance can also be improved.

  In the heat exchanger according to the third aspect of the present invention, since the plurality of tubes have the same width and the height of the tube facing the fluid inlet is the lowest, it faces the fluid inlet. The flow resistance of the fluid passing through the tube is the largest, and the fluid is difficult to pass. In addition, since the height of the tube is increased for each of the plurality of horizontal stages or for each horizontal stage as the distance from the fluid introduction port increases in the vertical direction, the fluid that passes through the tube as the distance from the fluid introduction port increases in the vertical direction. The flow resistance of the fluid becomes smaller and the fluid becomes easier to pass through. As a result, similar to the above, the fluid actively attempts to pass through a tube that is vertically away from the fluid inlet, thus suppressing the bias that a large amount of fluid flows into the tube facing the fluid inlet. it can. In addition, since the plurality of tubes have the same width and the height of the tube facing the fluid introduction port is the lowest, the amount of fluid flowing into the tube facing the fluid introduction port is reduced. The resistance when the fluid flows through the tube facing the fluid inlet increases and the speed of the fluid decreases. As a result, as described above, when the fluid passes through the tube facing the fluid inlet, the fluid is efficiently cooled or heated by the refrigerant or the heat medium. The performance can also be improved.

  In the intake air cooling device according to the fourth aspect of the present invention, since the hole area in the horizontal stage of the tube facing the fluid introduction port is formed to be the smallest, the intake air compressed out by the turbocharger is formed in the fluid introduction port. The flow resistance of the intake air passing through the opposite tubes is the largest, and the intake air is difficult to pass. In addition, since the hole area of the tube is formed so as to increase for each of the plurality of horizontal stages or for each horizontal stage as the distance from the fluid introduction port increases in the vertical direction, the intake air that passes through the tube as the distance from the fluid introduction port increases in the vertical direction. As the flow resistance decreases, the intake air becomes easier to pass. As a result, since the intake air actively attempts to pass through the tube that is separated from the fluid introduction port in the vertical direction, the bias that a large amount of intake air flows into the tube facing the fluid introduction port can be suppressed. Accordingly, since the intake air flows in a distributed manner across the plurality of tubes, the cooling performance of the intercooler can be improved. Further, since the hole area in the horizontal stage of the tube facing the fluid introduction port is formed to be the smallest, the amount of intake air flowing into the tube facing the fluid introduction port decreases, and the tube where the intake air faces the fluid introduction port The resistance at the time of circulation increases and the speed of intake decreases. As a result, since the intake air is efficiently cooled by the outside air when the intake air passes through the tube facing the fluid inlet, it is possible to improve the overall cooling performance of the intercooler.

  In the intake air cooling device of the fifth aspect of the present invention, since the hole area in the horizontal stage of the tube facing the fluid introduction port is formed to be the smallest, the flow resistance of EGR gas passing through the tube facing the fluid introduction port The EGR gas is difficult to pass through. Further, since the hole area of the tube is increased for each of the plurality of horizontal stages or for each horizontal stage as the distance from the fluid introduction port increases in the vertical direction, EGR passes through the tube as the distance from the fluid introduction port increases in the vertical direction. The gas flow resistance becomes smaller and the EGR gas easily passes. As a result, since the EGR gas actively attempts to pass through the tube that is separated from the fluid inlet in the vertical direction, it is possible to suppress the bias that a large amount of EGR gas flows into the tube facing the fluid inlet. Accordingly, since the EGR gas flows in a distributed manner across the plurality of tubes, the cooling performance of the EGR cooler can be improved. Further, since the hole area in the horizontal stage of the tube facing the fluid inlet is formed to be the smallest, the amount of EGR gas flowing into the tube facing the fluid inlet is reduced, and the EGR gas faces the fluid inlet. The resistance at the time of flowing through the tube increases and the speed of the EGR gas decreases. As a result, since the EGR gas is efficiently cooled by the outside air when the EGR gas passes through the tube facing the fluid inlet, the overall cooling performance of the EGR cooler can be improved.

It is the sectional view on the AA line of FIG. 2 which shows the intercooler which is an intake air cooling device of the engine of 1st Embodiment of this invention. It is a B arrow line view of FIG. It is a figure which shows the structure of the intake system of the engine containing the intercooler. It is CC sectional view taken on the line of FIG. 5 which shows the intercooler which is an intake air cooling device of the engine of 2nd Embodiment of this invention. It is D arrow line view of FIG.

Next, an embodiment for carrying out the present invention will be described with reference to the drawings.
<First Embodiment>
As shown in FIG. 3, the intake air cooling device of the diesel engine 11 includes an intercooler 13 that cools the intake air (intake air) compressed by the turbocharger 12. One end of an intake pipe 16 is connected to the intake port of the engine 11 through an intake manifold 14, an air cleaner 17 is attached to the other end of the intake pipe 16, and the intercooler 13 is provided in the middle of the intake pipe 16. One end of an exhaust pipe 19 is connected to the exhaust port of the engine 11 through an exhaust manifold 18 and the other end of the exhaust pipe 19 is opened to the atmosphere. The turbocharger 12 compresses the turbine rotor blades 12a rotated by the energy of exhaust (exhaust gas) discharged from the engine 11 and the intake air supplied to the engine 11 connected to the turbine rotor blades 12a via a shaft 12b. A compressor rotor blade 12c. The turbine rotor blade 12a is rotatably accommodated in the turbine housing 12d, and the compressor rotor blade 12c is rotatably accommodated in the compressor housing 12e. The inlet of the turbine housing 12 d is connected to the exhaust manifold 18, and the outlet of the turbine housing 12 d is connected to the exhaust pipe 19. The inlet of the compressor housing 12e is connected to the intake pipe 16 on the air cleaner 17 side, and the outlet of the compressor housing 12e is connected to the intake pipe 16 on the intercooler 13 side.

  As shown in detail in FIGS. 1 and 2, the intercooler 13 is arranged between a plurality of tubes 21 a to 23 a extending in the horizontal direction and spaced apart in the vertical direction, and the tubes 21 a to 23 a. A plurality of fins 24 provided, a single inlet side tank 25 provided on the intake inlet side of the tubes 21a to 23a, and a single outlet side tank 26 provided on the intake outlet side of the tubes 21a to 23a. And have. A flat passage through which intake air passes is formed in the plurality of tubes 21a to 23a, and the plurality of fins 24 are formed of sine waves so as to alternately contact the adjacent tubes 21a to 23a with an interval in the vertical direction. It is formed in a corrugated plate shape. In addition, the inlet side tank 25 and the outlet side tank 26 are formed in a substantially rectangular parallelepiped shape, the inlet side tank 25 is connected in communication with all of the plurality of tubes 21a to 23a, and the outlet side tank 26 is connected to the plurality of tubes 21a to 21a. 23a is connected to all intake outlets. An intake inlet 25a for allowing intake air to flow into the inlet side tank 25 is formed in the upper part of the inlet side tank 25, and the intake inlet 25a is connected to the intake pipe 16 on the compressor housing 12e side. An intake exhaust port 26a for exhausting intake air from the outlet side tank 26 is formed in the upper portion of the outlet side tank 26, and the intake exhaust port 26a is connected to the intake pipe 16 on the intake manifold 14 side. In this embodiment, the fin is formed in a corrugated plate shape made of a sine wave, but may be formed in a corrugated plate shape made of a triangular wave.

  Of the plurality of tubes 21a to 23a of the intercooler 13, the hole area in the horizontal stage of the tube 21a facing the intake inlet 25a is formed to be the smallest, and the hole areas of the tubes 22a and 23a are increased as the distance from the intake inlet 25a in the vertical direction increases. Is configured to be larger for each of a plurality of horizontal stages. In this embodiment, the plurality of tubes 21a to 23a have the same length, and the plurality of tubes 21a to 23a have the same height. Moreover, the tube 21a-23a in each horizontal stage is provided in the width direction so that one or more may be provided so that it may be settled in the same width. However, in FIG. 1, when the distance from the left end to the right end of the tube groups 21 to 23 in each horizontal stage is set to be the same and a plurality of tubes are provided in the same horizontal stage, the interval between these tubes is The same setting is made for the entire tube group. Further, among the plurality of tubes 21a to 23a, the number of tubes 21a in the horizontal stage facing the intake inlet 25a is the largest, and as the distance from the intake inlet 25a in the vertical direction, the number of tubes 22a, 23a increases to a plurality of horizontal. It is configured to be reduced for each stage.

As a specific example, a case will be described in which a plurality of tubes 21a to 23a are provided in 24 stages at intervals in the vertical direction. Among these tubes 21a to 23a, a tube group of eight stages from the top is defined as a first tube group 21 in which three tubes 21a are provided in each horizontal stage. Further, the eight-stage tube group immediately below the first tube group 21 is defined as a second tube group 22 in which two tubes 22a are provided in each horizontal stage. Further, an eight-stage tube group immediately below the second tube group 22 is defined as a third tube group 23 in which one tube 23a is provided in each horizontal stage. That is, since the tube 21a~23a in each horizontal step is provided three to 1 present in the width direction to fit within the same width, the width of each tube 21a of the first tube group 21 and W _1, second the width of each tube 22a of the tube group 22 and W _2, when the width of each tube 23a of the third tube group 23 and W _3, relationship 3W ₁ <2W ₂ <W ₃ is satisfied. Since each tube 21a~23a height H (FIG. 1) are all identical, the open area of each tube 21a of the first tube group 21 and S _1, the hole area of each tube 22a of the second tube group 22 was a S _2, when the open area of each tube 23a of the third tube group 23 and S _3, the hole area of the tube 21a~23a per horizontal stage of the first to third tube group 21 to 23 3S ₁ < The relationship 2S ₂ <S ₃ is satisfied. The plurality of tubes may not be 24 stages, but may be 23 stages or less or 25 stages or more.

  The operation of the intercooler 13 configured as described above will be described. When the engine 11 is started, intake air (intake air) flows into the cylinder of the engine 11 through the air cleaner 17, the intake pipe 16, the compressor housing 12 e of the turbocharger 12, the intercooler 13, and the intake manifold 14, and fuel in the cylinder It is mixed and burned to generate exhaust (exhaust gas). The exhaust is discharged to the atmosphere through the exhaust manifold 18, the turbine housing 12d of the turbocharger 12, the exhaust pipe 19, and an exhaust treatment device (not shown). The energy of the exhaust discharged from the engine 11 rotates the turbine rotor blade 12a, and this rotational force is transmitted to the compressor rotor blade 12c through the shaft 12b, so that the compressor rotor blade 12c rotates. As a result, the intake air is compressed and its temperature rises, so that this high-temperature compressed intake air is cooled by the intercooler 13.

At this time, the three to one tubes 21a to 23a in the horizontal stages of the first to third tube groups 21 to 23 of the intercooler 13 are within the same width, and the first tube group 21 of the intercooler 13 facing the intake inlet 25a. The number of tubes 21a in each horizontal stage is the largest, three, and the number of tubes 22a, 23a is decreased every eight stages as the distance from the intake inlet 25a in the vertical direction increases. Specifically, in the first tube group 21 closest to the intake inlet 25a, the number of tubes 21a in each horizontal stage is three, and in the second tube group 22 slightly away from the intake inlet 25a, in each horizontal stage. Since the number of the tubes 22a is two and the number of the tubes 23a in each horizontal stage is one in the third tube group 23 farthest from the intake inlet 25a, the first to third tube groups 21 to 23 are included. The hole area for each horizontal stage has a relationship of 3S ₁ <2S ₂ <S ₃ . For this reason, the flow resistance of the intake air passing through each tube 21a of the first tube group 21 facing the intake inlet 25a is the largest, and the intake air hardly passes. In addition, the flow resistance of the intake air passing through the tubes 22a and 23a gradually decreases from the second tube group 22 to the third tube group 23 from the intake inlet 25a in a vertical direction, and the intake air is gradually increased. It becomes easier to pass. As a result, since the intake air actively attempts to pass through the tubes 22a and 23a that are separated from the intake air inlet 25a in the vertical direction, a large amount of intake air is supplied to the tube 21a of the first tube group 21 that faces the intake air inlet 25a. Can be suppressed.

  In addition, the three to one tubes 21a to 23a in the horizontal stages of the first to third tube groups 21 to 23 are within the same width, and the horizontal stages of the first tube group 21 facing the intake inlet 25a. The number of tubes 21a in the first tube group 21 is the largest, so that the amount of intake air flowing into each tube 21a of the first tube group 21 facing the intake inlet 25a is reduced, and this intake air is the first tube. The resistance at the time of flowing through each tube 21a of the group 21 increases, and the speed of the intake air decreases. As a result, when the intake air passes through the tubes 21a of the first tube group 21, the heat of the intake air is smoothly transferred to the tubes 21a and the fins 24 and quickly removed by the outside air. The cooling performance can be improved.

<Second Embodiment>
4 and 5 show a second embodiment of the present invention. 4 and 5, the same reference numerals as those in FIGS. 1 and 2 denote the same components. In this embodiment, the plurality of tubes 61a to 63a have the same length, and the plurality of tubes 61a to 63a have the same width. Of the plurality of tubes 61a to 63a, the tube 61a facing the intake inlet 25a is formed at the lowest height, and the tubes 62a and 63a have a plurality of horizontal stages as they move away from the intake inlet 25a in the vertical direction. It is configured to be higher every time or every horizontal stage.

As a specific example, a case where a plurality of tubes 61a to 63a are provided in 18 stages at intervals in the vertical direction will be described. The tube group of eight stages from the ones of these tubes 61a~63a the first tube group 61 to the height H ₁ is formed lowest of each tube 61a. The six-stage tube group immediately below the first tube group 61 is a second tube group 62 in which the height H ₂ of each tube 62 a is formed higher than the height H ₁ of each tube 61 a of the first tube group 61. Further, the four-stage tube group immediately below the second tube group 62 is a third tube group 63 in which the height H ₃ of each tube 63 a is formed higher than the height H ₂ of each tube 62 a of the second tube group 62. That is, since the widths W of the tubes 61a to 63a are all the same and H ₁ <H ₂ <H ₃ , the hole area of each tube 61a of the first tube group 61 is S _1, and the second tube group 62 the open area of each tube 62a of the S _2, when the open area of each tube 63a of the third tube group 63 and S _3, relationship S ₁ <S ₂ <S ₃ is satisfied. The configuration other than the above is the same as that of the first embodiment. In addition, a some tube may be 17 steps or less, or 19 steps or more instead of 18 steps.

The operation of the intercooler 53 configured as described above will be described. Each of the tubes 61a to 63a of the first to third tube groups 61 to 63 has the same width W, and the height of each tube 61a of the first tube group 61 facing the intake inlet 25a is H ₁ most. The tubes 62a and 63a are formed so that the height of the tubes 62a and 63a decreases every eight steps as the distance from the intake air inlet 25a increases in the vertical direction. Specifically, the height of the tube 61a is lowest form and H ₁ of each horizontal step in the closest first tube group 61 to the intake air introduction port 25a, the second tube group 62 have a distance from the suction inlet 25a The height H ₂ of the tube 62a in each horizontal stage is formed next lowest, and in the third tube group 63 farthest from the intake inlet 25a, the height H ₃ of the tube 63a in each horizontal stage is formed highest. The hole area for each horizontal stage of the first to third tube groups 61 to 63 has a relationship of S ₁ <S ₂ <S ₃ . For this reason, the flow resistance of the intake air passing through each tube 61a of the first tube group 61 facing the intake air inlet 25a is the largest, and the intake air hardly passes. In addition, the flow resistance of the intake air passing through the tubes 62a and 63a gradually decreases from the second tube group 62 to the third tube group 63 from the intake inlet 25a in the vertical direction, and the intake air is gradually increased. It becomes easier to pass. As a result, since the intake air actively attempts to pass through the tubes 62a and 63a that are separated from the intake air inlet 25a in the vertical direction, a large amount of intake air is supplied to the tube 61a of the first tube group 61 that faces the intake air inlet 25a. Can be suppressed.

The first to third tube 61a~63a the tube group 61 to 63 have the same width W, and height H ₁ of each tube 61a of the first tube group 61 that faces the intake air introduction port 25a is most When the intake air flows through the tubes 61a of the first tube group 61, the amount of intake air flowing into the tubes 61a of the first tube group 61 facing the intake inlet 25a is reduced. The resistance increases and the intake speed decreases. As a result, when the intake air passes through the tubes 61a of the first tube group 61, the heat of the intake air is smoothly transferred to the tubes 61a and the fins 24 and quickly taken away by the outside air. The cooling performance can be improved.

  In the first and second embodiments, the hole area of the tube is increased for each of the plurality of horizontal stages as the distance from the intake inlet is increased in the vertical direction, but the distance from the intake inlet is increased in the vertical direction. Accordingly, the hole area of the tube may be increased for each horizontal stage. Specifically, in the first embodiment, the configuration is such that the number of tubes decreases for each of a plurality of horizontal stages as the distance from the intake inlet increases in the vertical direction. You may comprise so that the number of may decrease for every horizontal stage. In the second embodiment, the height of the tube is increased for each of the plurality of horizontal stages as the distance from the intake inlet is increased in the vertical direction. However, the height of the tube is increased as the distance from the intake inlet is increased in the vertical direction. May be configured to be higher for each horizontal stage.

  In the first and second embodiments, the intake inlet is formed in the upper part of the inlet side tank and the intake outlet is formed in the upper part of the outlet side tank. And an intake outlet may be formed in the lower part of the outlet side tank. In this case, the eight-stage tube group from the bottom is the first tube group in which three tubes are provided in each horizontal stage, and the eight-stage tube group immediately above the first tube group is two in each horizontal stage. The second tube group is provided with a tube, and the eight-stage tube group immediately above the second tube group is a third tube group in which one tube is provided in each horizontal stage. The present invention can also be applied by forming the intake inlet at the upper part of the inlet side tank and forming the intake outlet at the lower part of the outlet side tank. This is because even if the intake exhaust port is formed in the lower part of the outlet side tank, if the intake introduction port is formed in the upper part of the inlet side tank, the intake air that has flowed into the upper part of the inlet side tank proceeds straight as it is. This is because it tends to flow into the water.

  Furthermore, in the first and second embodiments, the intercooler that cools the intake air compressed by the turbocharger is cited as the heat exchanger. However, the EGR gas that is recirculated from the exhaust passage of the engine to the intake passage. It may be an EGR cooler that cools the heat exchanger or other heat exchanger.

12 Turbocharger 13,53 Intercooler (Heat exchanger)
21a-23a, 61a-63a Tube 24 Fin 25 Inlet side tank 25a Intake inlet (fluid inlet)
26 Outlet side tank 26a Intake exhaust port (fluid exhaust port)

Claims (5)

A plurality of tubes (21a to 23a, 61a to 63a) in which a flat passage through which a fluid passes inside is formed, extending in the horizontal direction and spaced in the vertical direction, and these tubes (21a to 23a, 61a to 63a) and a plurality of fins (24) formed in a corrugated plate so as to alternately contact adjacent tubes (21a to 23a, 61a to 63a), and the tubes (21a to 63a) A single inlet-side tank (25) provided on the fluid inlet side of the plurality of tubes (21a-23a, 61a-63a) and connected to the fluid inlet of the plurality of tubes (21a, 61a-63a), and the tubes (21a A single outlet side tank (26) provided on the fluid outlet side of the plurality of tubes (21a to 23a, 61a to 63a) and connected to the fluid outlet of the plurality of tubes (21a to 23a, 61a to 63a), and the inlet side A fluid inlet (25a) formed in the tank (25) for introducing the fluid into the inlet side tank (25), and formed in the outlet side tank (26) and forward from the outlet side tank (26). In the heat exchanger having a fluid outlet for discharging the fluid and (26a),
Of the plurality of tubes (21a-23a, 61a-63a), the hole area in the horizontal stage of the tubes (21a-23a, 61a-63a) facing the fluid inlet (25a) is formed to be the smallest, and the fluid The heat is characterized in that the hole area of the tubes (21a to 23a, 61a to 63a) is configured to increase for each of the plurality of horizontal stages or for each horizontal stage as the distance from the introduction port (25a) increases in the vertical direction. Exchanger. The plurality of tubes (21a to 23a) each have the same length,
The plurality of tubes (21a to 23a) each have the same height,
Single or multiple tubes are provided in the width direction so that the tubes (21a to 23a) in each horizontal stage fit within the same width,
Among the plurality of tubes (21a-23a), the number of tubes (21a) in the horizontal stage facing the fluid inlet (25a) is the largest, and as the distance from the fluid inlet (25a) increases in the vertical direction. The heat exchanger according to claim 1, wherein the number of the tubes (22a, 23a) is configured to be reduced for each of a plurality of horizontal stages or each horizontal stage. Each of the plurality of tubes (61a to 63a) has the same length,
The plurality of tubes (61a to 63a) each have the same width,
Of the plurality of tubes (61a-63a), the height of the tube (61a) facing the fluid inlet (25a) is formed to be the lowest, and the tube as the distance from the fluid inlet (25a) increases in the vertical direction. The heat exchanger according to claim 1, wherein the height of (62a, 63a) is configured to be higher for each of a plurality of horizontal stages or for each horizontal stage.   An intake air cooling device for an engine, wherein the heat exchanger according to any one of claims 1 to 3 is used as an intercooler (13, 53) for cooling the intake air compressed by the turbocharger (12).   An engine intake air cooling apparatus, wherein the heat exchanger according to any one of claims 1 to 3 is used as an EGR cooler for cooling EGR gas recirculated from an engine exhaust passage to an intake passage.

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